Perforating machine



Jan. 16, 1934. F. B. KEALL 1,943,441

PERFORATING MACHINE Filed July 28, 1930 5 Sheets-Sheet l WI/E/VTUF m gwg Ian. 16, 1934. B KEALYL 1,943,441

PERFORATING MACHINE Filed July 28, 1930 5 Sheets-Sheet 2 48'45-1ZUL k HQQLQ Jan. 16, 1934. F. B. KEALL 1,943,441

PERFORAT ING MACH INE Filed July 28, 1930 5 Sheets-Sheet 3 WVE/VTUF MNJ-K Rs HQQLLQ QEQALQQMW Jan. 16, 1934. B KEALL 1,943,441

PERFORATING MACHINE 5 Sheets-Sheet 4 Filed July 28, 1930 Figll. Fig. 10.

29 E 30 3 2 JJ bfl WVENTUF 'Q M 5. mm

Jan. 16, 192248 F B KEALL 1,943,441

PERFORATING MACHINE Filed July 28, 1950 5 Sheets-Sheet 5 VVI/E/VTUF Patented Jan. 16, 1934 UNITED STATES PATENT OFFICE PERFORATIN G MACHINE Application July 28, 1930, Serial No. 471,168, and in Great Britain August 15, 1929 33 Claims.

This invention relates to perforating machines of the type in which the work is advanced progressively to a punching tool, or a gang of punching tools arranged to form an ornamental de- 5 sign. An important field of use for such machines is in perforating the uppers of boots and shoes and for purposes of illustration the invention will be described in that connection.

The present invention contemplates the provision of an improved perforating machine capable of operating smoothly and accurately at high speed and adapted to handle the work in a convenient manner for the operator. The construction of the machine moreover, is such as to reduce to a minimum the tendency of wear in its moving parts by eliminating excessive and unbalanced pressure and in general to relieve the work-feeding instrumentalities of strain during the feeding Operation.

. In machines of this type as heretofore constructed, it has been the practice to feed the work intermittently by a single feeding step between consecutive punching operations. As .distinguished from such feeding prooednre, it is now proposed to feed the work in .a substantially continuous movement through the machine, To this end, an important feature of the invention consists in utilizing the usual anvil, punch and presser foot in a cooperative manner for continuously i feeding the work in addit on to e r un ion o -0 punching and positioning the work. For example, the punch and presser foot may be arranged-for movement toward the work upon the anvil for punching and positioning the work and may then be moved one after the other transversely to feed the work in cooperation with the anvil. s iherein shown, the punch is moved transversely :with the work after the punching operation and then the presser foot and ,anvil are moved with o the work between them, carrying the work further and in the same direction while the punch is re,- turned to its initial position in readiness for :punehng and feeding operations. By this airrangement, and without the provision of additional instrumentalities, a continuous feed of the work is secured by the supplementary movements of the usual machine parts. and each movement thereof is of limited extent or amplitude so that it may be effected smoothly at high speed.

Another feature of the invention consists in a single controlling device arranged to adjust the amplitude of feed of the supplementary feeding elements. This is advantageous in giving the machine a flexibility of adjustment and a wide range of feeding capacity. Preferably and as herein shown, the controlling mechanism is so designed that if desired the feeding movement of the supplementary members may be reduced to zero, and the machine thus adapted for hand feeding where this is required.

Other features of the invention relate to the punch and the novel actuating mechanism associated therewith. As herein shown, I provide separate cams for effecting the punching operation and for controlling the position of the punch during the feeding operation and on this account I am enabled to secure an independent adjustment of the punch in these two important positions in its cycle.

Still other features of the invention relate to 0 novel mechanism for supplying and feeding a paper strip to the anvil whereby it is possible properly to correlate the movement of the paper strip with the continuous feeding movement of the work. As herein shown, the same actuating 5 means is utilized for the work feeding instrumentalities and the paper strip feeding mechanism, and this arrangement ofiers a convenient means for regulating the rate of strip feed in accordance with the work feed.

These and other features of the invention will be best understood and appreciated from the following description of a preferred embodiment thereof, selected for purposes of illustration and sho n the cco pa dr w in wh Fi is a an ew bf a ma e F a 2. new n om e v on;

Fig. 3 is a view in end elevation, partly in sece and ona a e r cale:

Fig. 4 is a sectional view on the line 44 of :3;

Fig, 5 is a view in end elevation, partly in section, of the work feed operating mechanism of t ma h ne Fig. 6 is a plan view, partly in section, of the mechanism shown in Fig. 5 together with a part of the paper strip feeding mechanism;

' Fig :7 is a fragmentary view, partly in section, of some of the parts shown in Fig. 6;

Fig. 8 is a sectional view on the line 8-8 of Fig. 3;

Fig. 9 is a plan view, partly in section, of the punch operating mechanism and on an enlarged scale;

Fig. 10 is a View in front elevation of the edge guide of the machine;

Fig. 11 is a View in end elevation, partly in section, of the guide;

Fig. 12 is a plan view of the paper strip feedi g mecha ism an Fig. 13 is an end view, partly in section, of the mechanism shown in Fig. 12.

The machine herein illustrated is provided with a frame having a base 3 and an overhanging arm 2. The main driving shaft together with the punching mechanism, the presser foot and edge guide are mounted in the overhanging arm while the anvil and paper feeding mechanism are mounted in the base. The base is provided with a flat work table 5 upon which the work is fed to the machine in the space beneath the overhanging arm 2. The machine is shown in Fig. 2 in the position which it presents to the operator, the work being fed progressively from front to rear.

In the overhanging arm 2, journaled in suitable bearings, is provided the main driving shaft 6. At its right-hand end it is provided with a clutch, which may be of any commercial type, such as that shown, for example, in copending application of Ricks and Minett, Serial No. 435,985, filed March 15, 1930, and which is designed to bring the driving shaft to rest in a predetermined position whenever the treadle is released, as is customary in machines of this type.

Mounted for vertical reciprocation in the lefthand end of the overhanging arm 2 is a punch 7. The punch is moved vertically to perforate the work and then, while in engagement with the work, it is moved toward the rear to impart a feeding movement theretoj In the base 3 of the frame beneath the punch is arranged an anvil 8 against which the punch operates and against which the work is at times held by a presser foot 9, also mounted in the arm 2. The punch 7 herein shown is a single punch of circular outline but a multiple punch may be used in ornamental perforating. It is mounted in the lower end of a frusto-conical block 10, see Figs. 3 and 8, which is clamped to the enlarged lower end 11 of a vertically disposed punch spindle 12 by means of a clamping plate 13, having an inner beveled face 15 which engages a beveled face 16 extending around the block 10 and presses the latter against oppositely beveled faces of lugs 17 on the enlarged end 11 of the spindle. The clamping plate 13 is secured to the latter by a screw 14. The punch '7 is tubular and. the punchings formed by it in the work are led upwardly in a passage formed in the block 10 and discharged through an opening with which the enlarged end 11 is provided.

The punch spindle 12 is mounted. fora limited movement of free rotation in a vertical tubular punch bar 18 but is secured thereto for positive vertical movement therewith. To this end, the spindle 12 is provided with a reduced stem 4 which passes through a bore in the upper solid portion of the tubular punch bar and is provided at its upper end with a nut and washer. The punch spindle is thus free to rotate about its own axis with the work during the operation of feeding a curved piece of work. After being thus rotated, the punch spindle is returned to its normal position by the engagement of a squared face on the lower end of a rocker lever 19 with a flat surface 20 on the spindle. It will be understood that the tubular punch bar 18 is provided with an opening opposite to the flat surface 20 through which the end of the rocker 19 may pass. The rocker lever is mounted upon a horizontal pivot 21 extending lengthwise of the arm 2 of the frame. A spring-pressed plunger 22 engages the outer face of the lower arm of the rocker, tending at all times to move it inwardly and hold the upper end in engagement with an adjustable stop 23 threaded into a portion of the arm 2 of the frame. The stop 23 thus adjustably determines the initial position of the rocker member while the spring-pressed plunger 22 allows it to yield slightly near the end of the return movement of the punch and after the spindle positioning faces engage each other. The yield allows the lever 19 to maintain its straightening effect on the punch by following the latter during a part of its movement in the direction of the feed.

The tubular punch bar 18 is vertically slidable in a punch bar carrier 24 which is movable transversely to feed the work rearwardly, as seen in Fig. 2, or from right to left, as seen in Fig. 8. The punch bar 18 at its upper end has projecting from each side horizontally extending lugs 25 perforated to receive vertical plungers 28 which are encircled by compression springs 26 bearing against the under side of the lugs 25 and acting at all times to move the punch bar upwardly. The springs 26 at their lower end bear against heads 2'? of the plungers 28 and these heads rest upon rollers 29 which are arranged to run upon flat surfaces formed on blocks 30 secured to the arm 2 of the machine as the carrier member 24 is moved transversely in its work feeding movements. By this arrangement the downward thrust of the springs 26 is taken up through the antifriction rollers'29 by the machine frame in a balanced manner without any tendency toward cramping the movement of the punch bar or creating undue wear. The rollers 29 are prevented from displacement beneath the heads 27 of the plungers by flanges 31 formed on the blocks 30 in front of the rollers and projections 32 on the carrier 24 behind the rollers.

Near the lower end of the carrier 24 is attached a horizontal shaft 33 which extends forwardly and rearwardly of the machine'and. is slidingly mounted in stationary bearings 34 formed on the arm 2 of the frame. The rear end of the shaft 33 is connected to mechanism for moving the carrier 24 forwardly and rearwardly, as will be presently described. In its feeding movement the carrier is guided partly by the shaft 33 and partly by an upwardly-projecting tongue 35 which at the upper part of the carrier moves in a horizontal guideway formed in the arm 2 of the frame.

The punch bar 18 is moved downwardly in its carrier 24 to effect the punching operation by a cam lever 35 mounted to rock about a horizontal shaft 37 located parallel to and above the driving shaft 6 in the arm 2 of the frame. The cam lever 36 has a forwardly-extending arm in which is mounted an anti-friction roll 38 which bears upon a hardened cap 39 in the top of the punch bar 18. The rcarwardly-extending arm of the lever 36 carries a transversely-extending stud 40 (Fig. 9) upon the ends of which are mounted cam rolls 41 and 42 retained in place by screws 46 threaded into the ends of the stud. These cam rolls 41 and 42 are engaged by cams 170 and 172 (Figs. 3 and 9) fast on the driving shaft 6 of the machine. The cam lever 36 is mounted on an eccentric portion of its shaft 37 and the shaft may be rocked by a thumb screw 43 engaging at its lower end a squared face 1'73 formed in the shaft for the purpose of controlling the position of the punch vertically at the bottom of its punching stroke. A spring (not shown) holds the squared face of the shaft against the thumb screw 43 so that when the latter is turned reversely the shaft 37 will rotate to follow it.

The cam roll 41 is mounted on an eccentric portion 44 of the stud and the cam roll 42 is mounted on a sleeve 45 on a concentric portion of the stud 40. The cam 172 which acts on the cam roll 42 causes the punch to be depressed to punch the work, having a single throw in its periphery for this purpose. The cam 170 which acts on the cam roll 41 has a portion of its periphery effective to control the lift of the punch after the punching operation to release the punch from the anvil during the feeding movement. The stud 40 which carries the cam rolls has secured to it an upwardly-projecting arm 47 which is held by a spring 48 against a thumb screw 49 carried by the cam lever 35. By adjusting the thumb screw 49 the stud 40 may be rocked and the roll 41 may thus be adjusted with respect to the lever 36 to control the lift of the punch heightwise of the anvil during the feeding operation. The lift of the punch upon its return movement after the feeding operation may be adjusted by a thumb screw 50 (Fig. 8) threaded into a portion of the arm 2 of the frame and arranged to engage a lug 51 on the cam lever 36. The thumb screw 50 may, if desired, be so set that the punch rises above the work by a slight distance only and the punch may then be used as a gage for positioning the work on the table. This is a convenient arrangement where single punching opertions are to be performed at determined irregularly spaced positions on the work.

It will thus be seen that by using the thumb screws 43, 49 and 50, it is possible to secure an independent adjustment of the limit of movement of the punch in the punching operation, of the anvil-releasing position of the punch during the feeding operation and of the position of the punch heightwise of the anvil after the feeding operation. The first is secured through the thumb screw 43 by rocking the eccentric shaft 37 which carries the cam lever 36; the second adjustment is secured through the thumb screw 49 by rocking the cam lever stud 40 and changing the position of the cam roll 41; the third adjustment is secured through the thumb screw 50 which acts as a positive stop to limit the lifting movement of the cam lever 36. The two latter adjustments are, of course, somewhat affected by turning the thumb screw 43 but such variation as is caused by movement of the thumb screw 43 is compensated for in the individual setting of the thumb screws 49 and 50.

The mechanism for feeding the punch bar carrier 24 transversely in the work feeding operation will now be described. This is effected through a tubular rock shaft 54 (Figs. 1, 5 and 6) which is oscillated through cam connections with the main driving shaft 6 of the machine and connected at its left-hand end to the carrier 24. The tubular shaft 54 is disposed horizontally in bearings which project rearwardly from the arm 2 of the machine frame. The shaft 33, which is secured to the punch bar carrier 24, is connected at its rear end to a link 52 (Fig. 3) which, in turn, is connected to an arm 53 depending from the left-hand end of the tubular shaft 54. Projecting substantially horizontally from a hub 55 fixed upon the shaft 54, at the right-hand end thereof, is a second arm 56 to which is pivotally connected one end of a downwardly-inclined link 57. The link 57 passes between the driving shaft 6 where it is connected by a pivot 70 to an upwardly-inclined link 59 connected at its right-hand end,

as seen in Fig. 5, to onearm of' a feed adjusting lever 63. A second link 58 is also connected to the lower end of the link 57 by the pivot 76. The link 58, as shown in Fig. 6, extends rearwardly and upwardly from the pivot '70 and is connected at its upper end to a cam lever 60 extending upwardly from a horizontal shaft 61 to which it is secured and which extends longitudinally of the machine below and between the driving shaft 6 and the tubular shaft 54. The cam lever 60 carries a cam roll 196 which runs in a cam groove in a cam 62 fast upon the driving shaft 6. The cam roll 196 of the cam lever 60 is located substantially opposite to the point of pivotal connection between the cam lever 60 and the link 58. It will be seen that when the cam lever 60 is oscillated by the cam 62, its motion will be transmitted through the link 58 to the pivot 70 and through the link 57 and arm 56 to the tubular rock shaft 54, and thence through the arm 53 and link 52 to the carrier 24.

When the punch is in its initial or punching position, corresponding to its right-hand position as seen in Fig. 3, the pivotal connection of the link 57 and the arm 56 and the pivotal connection of the link 58 and the cam lever 60 are in axial alignment, so that movement of the other end of these links by the feed adjusting lever 63 through the link 59 does not alter the position of the punch. Therefore, the position in the machine at which the punching operation takes place re mains fixed for all different lengths of feed. The feed adjusting lever 63 has an arm 64 projecting forwardly of the machine and into this is threaded a thumb screw 65. The thumb screw 65 passes through an arcuate slot 66 in the front of the arm 2 of the frame. A washer 67 is interposed between the head of the thumb screw and the curved surface of the arm 2 and is provided with a pointer 68 cooperating with an index scale 69 indicating the length of feed corresponding to the different settings of the adjusting lever 64. The feed is adjusted by loosening the thumb screw 65 and swinging the lever over the concentric face of the frame and the lever may be locked in adjusted position by the clamping action of the screw against the frame. The length of the feeding step may be reduced to zero if desired for such single punching operations as above referred to, by swinging the lever 63 downwardly, as seen in Fig. 5, until the pivot 70 of the links 57, 58 and 59 is carried into axial alignment with the shaft 61.

As already stated, the feeding operation is effected in consecutive steps, one of which is carried out by the movement of the punch just described and the second of which is carried out by the cooperative action of the presser foot 9 and the-anvil 8. The presser foot is fixed on the lower end of a vertically-disposed presser bar 71 (Fig. 3) which near its lower end is guided in a vertically-disposed slot 72 formed in part by one of the bearing members 34 and in part by a face plate 73 attached thereto. The presser foot 9 is designed to engage the work close to and at the left side of the punch, as shown in Fig. 3. The upper end of the presser bar 71 is pivotally connected by a pin 74 to a cam lever 75 pivotally mounted upon a horizontally-disposed shaft 76 extending longitudinally of the machine parallel to and above the driving shaft 6. The cam lever 76 carries an intermediate cam roll 77 which is held in engagement with the periphery of a cam 174 on the left-hand end of the driving shaft 6 by a tension spring, not shown. The vertical movement of the presser foot in en aging and disengaging the work is thus controlled by the cam 1'74; and the spring acting in opposition T5 thereto.

Transverse feeding movement is imparted to the presser bar '71 by mechanism which will now be described. The presser bar is connected near its lower end by a rearwardly-extending link 78 to the lower end of an arm 79 depending from a solid shaft 80 arranged concentrically within the tubular feed shaft 54. The shaft 89 has an arm 81 (Figs. 5, 6 and '7) secured thereto which extends forwardly through an opening in the tubular shaft 5 1 and which at its forward end has a gear segment 82 meshing with a gear segment 83 on the rearwardly-extending arm of a lever 84. The lever 84 is journaled upon a shaft 85 extending longitudinally of the machine beneath and to the rear of the main driving shaft 6.' The forwardly-extending arm 86 of the lever is pivotally connected to a link 87 extending upwardly and rearwardly over the driving shaft. The upper end of the link 8'7 is pivotally connected. by a common pivot to links 88 and 89. The link 88 extends down wardly and rearwardly and is pivotally connected to an arm on the feed adjusting lever 63 hereinabove described. The link 89 extends down- ;wardly and forwardly and is pivotally connected to a depending cam lever 90 fast upon a shaft 91 extending longitudinally of the machine and mounted in hearings in the arm 2. The cam lever 90 carries a cam roll 92 which runs in the same cam groove as the cam roil associated with the punch feed mechanism but it is positioned 180 in advance of the latter cam roll. When the presser foot 9 is in its forward position, the pivot connecting the arm 86 of the se ment-carrying lever and the link 8'7 and the pivot connecting the link 89 and the cam lever 90 are in axial alignment, and if the feed adjusting lever 63 is then adjusted no transverse movement is imparted to the presser foot. As in the case of the punch, therefore, any adjustment of the transverse feeding movement of the presser foot affects only the final position of the presser foot at the end of its feeding stroke. If, as above suggested, the feed adjusting lever 63 is swung to bring the pivot '70 into axial alignment with the axis of the shaft 61 and thus eliminate the feeding movement of the punch, the pivot connecting the links 87, 88 and 89 is brought into axial alignment with the shaft 91 and the feeding movement of the presser foot is similarly eliminated.

The segment-carrying lever 8486 has pivotally connected to it a depending link 93 which at its lower end, see Fig. 3, is pivotally connected to an arm 94 secured to the right-hand end of a horizontal shaft 95 mounted to rock in bearings within the base 3 of the frame and extending longitudinally of the machine. Secured to the left-hand end of the shaft 95 is an upwardlyprojecting arm 96 which has at its upper end a roll arranged to run in a vertical slot 9'? in the lower portion of the anvil 8. By this means the anvil 8 is reciprocated horizontally in synchronism with the movement of the presser foot 9. The anvil 8 comprises a substantially rectangular block which is guided in'its horizontal movement in ways formed in the base 3 of the machine and is supported upon antifriction rollers 98 and 99.

The work-feeding movements of the punch '7 on the one hand and of the presser foot 9' and anvil 8 on the other hand are timed so that apparent that if desired the feeding movement.

due to the presser foot and anvil may overlap the feeding movement due to the punch alone, since the difierent feeding members travel at substantially the same rate of speed. Where the feeding movements overlap in this manner, the work will be fed at one time by the punch, another time by the presser foot and anvil and momentarily by all three elements together. The movement of the feed adjusting lever to vary the length of the feed in each cycle of the machine will cause the effective movement of the different feeding members to be adjusted by equal amounts.

The movement of the presser foot in the direction of feed may, alternatively, be obtained as a result of its clamping the work against the anvil and being thereby moved with the anvil and work during the feed. By such an arrangement some of the parts which move the presser forwardly and rearwardly are dispensed with. The cam lever '75 by which the up and down movements of the presser are eifected, in this case, has a depending arm and between the lower end of this arm and the presser bar is interposed a compression spring tending to move the presser bar forwardly of the machine against a stop on the frame. As the presser bar is moved down into engagement with the work, lower end of the depending arm of the cam lever swings away from the bar and the pressure of the spring is somewhat relieved. As the presser bar is movedrearwardly with the work and anvil, the spring is compressed and as soon as the presser bar begins to lift and is free to move back again it is so moved forwardly of the machine by the spring into engagement with the stop on the frame.

t the right-hand side of the line of feed of the punch and in advance of the punching position is provided. an edge guide (Figs. 10 and 11) against which the edge of the work is guided during the operation of the machine. The guide surface 100 is formed on the lower end of an arm 101 which extends upwardly and rearwardly from its lower end and is adjustably connected to a bracket 102. The bracket in turn is supported by a horizontal shaft 113 extending longitudinally of the machine and secured to the side of the arm 2 of the frame. The work guiding face 100 extends upwardly from a foot plate 103 which is formed on the lower end of the arm 101 and the lower face of the foot plate is shaped, as shown in Fig. 10, to bridge a paper strip which passes over the anvil 8 and against which the punch operates. The arm 101 is adjustable in the direction of feed to bring the foot plate 103 nearer to or further from the punch. To this end, the arm 101 is provided with a vertical rib 105 arranged to enter a corresponding vertical groove in the bracket 102. The arm 101 is adjustably retained in place by a thumb screw 106 passing through the arm and threaded into the bracket 102. The arm 101 is held at all times forwardly against the head of the thumb screw 106 by a compression spring ment with the guiding surface 100. The foot 108 is adjustable vertically upon the arm 101 by means of a stud 109 rotatably mounted in the arm and having an eccentric portion which enters a slot in the upper end of the foot. A guide pin 111 projects from the arm 101 into a second slot 112 and a spring (not shown) extending between the arm 101 and the foot 108 holds the foot up against the eccentric portion of the stud 109.

The bracket 102 which carries the edge guide and its associated parts has a hub 114 through which passes the shaft 113. Above the shaft 113 the hub is provided with a lug 115 which, when the edge guide is in operative position, may be engaged with a face 117 on the arm 2 of the frame and clamped thereagainst by a thumb screw 118 threaded through the bracket below the shaft 113 and engaging the frame. When the screw 118 is loosened, the bracket 102 is free to be moved along the shaft 113 toward the right, as seen in Fig. 2. In this movement the lug 115 may be carried beyond the end of the face 117 and opposite to a depression in the arm 2 of the frame: In this position the bracket 102 may be swung substantially 180 about the axis of the shaft 113 and carried into an inoperative position. When this has been reached, the arm 101 extends upwardly close to the surface of the arm 2 of the frame so that the space beneath the arm is left clear for the passage of the work when, for instance, punching is being performed at the interior of a large work piece. When the bracket 102 has been swung into its inoperative position, it may be slipped to the left again on the shaft 113 and this movement brings the lug 115 opposite to a face 116 on the arm of the frame beneath the bracket shaft 113 and by engagement with this surface the bracket is maintained in its inoperative position. When the bracket is swung and slipped on the shaft 113 back to its operative position and clamped against the face 117, the guiding surface and its associated parts are restored precisely to their adjusted operative position in the machine and the work may proceed without further delay.

The paper backing strip 104 is drawn from a supply reel 120 which is rotatably mounted upon the vertically-disposed hub 121 of a reel-supporting disk 122. The hub is mounted on a vertical stud 123 projecting upwardly from a bracket 124 secured to the rear of the machine base 3 below the table 5. The supporting disk 122 is held against rotation by a pin 125 projecting upwardly from the bracket 124 and entering a slot in the disk. The disk 122 may be adjusted upwardly without losing its connection with the stationary pin 125. The disk 122 is provided upon its upper face with a leather ring 126 on which the reel 120 rests and which frictionally prevents the reel from over-running and the strip 104 thus becoming loose. A screw 127 is threaded vertically into the hub 121 and bears at its lower end against the stud 123. By turning the screw 127 the supporting disk 122 and the reel carried thereby may be raised or lowered to bring the paper strip into proper alignment with a guide roll 129 which is rotatably mounted upon a spindle 130 carried by the bracket 124.

From the guide pulley 129 the paper strip 104 makes a quarter turn and passes forwardly beneath the table 5 and the anvil 8 and reaches a second guide pulley 131 at the front of the machine, see Fig. 3. The guide pulley 131 is located beneath the table 5 and is loosely mounted on a ing in the table 5 through which the anvil 8 pro- J jects ad is then led rearwardly over the surface of the anvii. From the anvil the paper strip passes down through the opening in the table and into engagement with the strip feeding roll 134 (Fig. 12).

feeding mechanism of the machine, as will present y appear, and is rotatably mounted on a spindle 135 projecting upwardly from the bracket 124 at an angle of substantially 15 to the vertical. roll 134 by a presser roll 136 which is rotatably mounted on a stud 137 carried by a pivoted presser arm lhe arm 138 is mounted to swing upon the upper end of the spindle 130 of the The feed roll 134 is driven from the The strip 104 is held against the feed guide pulley 129 and the axis of the presser roll 136 is parallel to the axis of the feed roll when the two are in engagement with the strip 104. The presser roll 136 is held against the strip by a tension spring 139 attached to the arm 138 and to the bracket 124. From the feed roll the paper strip passes to a second reel 140 upon which the used paper strip is wound; The reel 140 is also located beneath the table 5 and its axis is parallel to the axis of the feed roll 134. It is driven frictionally from the feeding mechanism 7 of the machine, as will presently appear, and is furnished with an adjusting screw 175 by which it may be adjust-ed up or down in a similar manner to the supply reel 120.

The drive for the strip feeding mechanism is effected by a round belt run over grooved pulleys, the belt being driven through connections with the oscillating lever 84 and the oscillating tubular shaft 54 which form a part of the work feeding mechanism of the machine. By this arrangement the rate of the strip feed is varied in accordance with the rate of the work feed, with a resulting economy in the use of the backing strip. The reel 140, however, is frictionally driven at such a rate that it tends to wind up the strip a little faster than it is fed by the punch and presser foot. The strip is thus kept taut and prevented from accumulating between the reel and the punch, the friction drive of the reel 140 slipping slightly during the feeding operation.

As has been already set forth, the punch and presser foot act alternately to feed the work continuously and a continuous rotary drive for the paper strip is derived from the actuating shafts of these mechanisms by means of two roller clutch devices which act alternately upon the same driven member. I

The tubular shaft 54 or" the punch feed mechanism at its right-hand end is reduced in diameter and formed as a solid shaft 141, to which is pinned a disk 142. A pin 143 projecting from the disk 142 acts to drive a clutch disk 144 which in its oscillation in one direction advances a clutch cage member 152 which is journaled to turn upon the hub of the disk 142. It wfll be from the flange of a sleeve 149 iournaled upon the shaft 141. The sleeve 149 is clamped within a collar 148 which, as shown in Fig. '1, is provided with a gear segment 147. The gear segment 147-meshes with a gear segment 146 formed on an arm 145 which projects from the same hub as the segment arm 84 and the arm 85 above mentioned and which is oscillated in time with the presser foot movement by the cam lever 90. It will be apparent, therefore, that the cage memher 152 is rotated. first by the movement of the clutch disk 144 under the actuation of the cam lever 60 and then by the clutch disk 151 under the actuation of the cam lever 90.

The cage member 152 has pinned to its outer face a gear 153 meshing with a gear 154 upon the inner end of a spindle 156 which is rotatably mounted in a bracket'projecting from the base 3 of the frame. The spindle 156 carries also a grooved pulley 155 which constitutes the driving pulley for a round belt 157, shown in Fig. 12. The rewinding reel 140 on which the strip is wound and the feed roll 134 are driven by the round belt 157, which upon leaving the pulley 155 is led around pulleys 158 and 159 connected respectively with the reel 140 and the feed roll 134. This-belt is guided by idler pulleys 160 and 161 (Fig. 2) journaled in brackets on the machine frame and also passes about a tightener pulley 163 carried by an arm 164 pivoted to the bracket 124 at the rear of the machine frame and urged outwardly by a tension spring so as to maintain the belt under tension. The pulley 158 is formed on the supporting disk 200 for the reel 140 and the reel is frictionally driven by a leather ring fixed to the rotatable support and against which the reel 140 is pressed by a weight 202.

The extension 128 of the work table extends rearwardly over the paper reels and covers the strip handling mechanism and the feed parts, and thus leaves the top of the table clear for the passage of the work.

The operation of the machine herein disclosed 3 willbe apparent from theforegoing description but may be summarized as follows. The operator presents the work to the machine, gaging its edge by the guide surface 100 of the edge guide, and advanced so that the point at which it is desired to form the first perforation is directly beneath the punch. Upon depressing the treadle to trip the clutch, the main shaft 6 is at once rotated and the punch depressed by the rocking of the cam lever 36 under the actuation of its associated cam 1'72 on the shaft 6. Immediately on the completion of the punching operation, the high portion of the cam 172 leaves its roll 42 and the spring plungers 28 are free to lift the punch, so as to release its pressure upon the anvil and to a height determined by the engagement of the cam 170 with the cam roller 41. The cam 62 then acts through the cam lever 60 to oscillate the tubular shaft 54 an angular distance determined by the setting of the feed adjusting lever 64. The corresponding oscillation of the arm 53 moves the carrier 24 with the punch rearwardly, feeding the work across the surface of the anvil 8. The oscillation of the tubular shaft 54 also rotates the cage m mber 152 of the clutch mechanism, which actuafes the belt drive of the paper feed mechanism, so that the paper strip 104 is advanced with the punch and the work. At the conclusion of the transverse feeding movement of the punch, the cam 1'70 permits the la.- ter to rise to its initial position as determined by the thumb screw 50 and a reverse oscillation of cam lever 90 is then oscillated to rock the shaft and move the presser foot rearwardly through its connection with that shaft. During the rearward movement of the presser foot, the oscillation of the flanged sleeve 194 carries the cage member 152 ahead another step so that the feed ing movement of the paper strip is continuous first with the punch and then with the presser foot. When the presser foot is about to release the work and return to its forward position, the punch 8 is again depressed and the cycle continued smoothly and without interruption.

Having thus described my invention, what I claim as new and desire to secure by Letters Patent is: a

1. In a perforating machine having a punch and a work support constructed and arranged to cooperate therewith in punching the work; mechanism for feeding the work step by step between" punching operations comprising means for moving the punch and the work support transversely one after the other, and means for maintaining the work in engagement with the work support during feeding movements of the latter.

2. A perforating machine comprising a punch and anvil relatively movable to punch the work, means for moving the punch transversely to feed the work, means for clamping the work on the anvil and means operable after the feeding movement of the punch for moving the anvil with the work clamped thereon to feed the work further in the same direction.

3. A perforating machine comprising a punch and anvil relatively movable to punch the work, means for moving the punch transversely to feed the work, and a presser foot movable to clamp the work against the anvil and then transversely with the anvil to feed the work while the punch remains in feeding engagement therewith.

4. A perforating machine having a work feeding device comprising a punch, a second workfeeding device comprising a presser member and an anvil, means for operating said devices consecutively to feed the work, and a single controlling device for regulating the amplitude of feed of both devices.

5. A perforating machine having a punch constituting a work feeding device, an anvil and a presser member constituting a second work-feeding device, said devices being movable consecutively to feed the work, and a single device adjustable for simultaneously varying the ampli tude of feed of both devices.

6. A perforating machine having a punch, an anvil and a presser foot cooperating to position and punch the work, means for moving the punch transversely to feed the work, means for moving the anvil and presser foot transversely also to feed the work, and a single controlling device for regulating the amplitude of feed of each of said elements.

'7. A perforating machine having a punch arranged for reciprocation toward and from the work to effect a punching operation, an anvil against which the punch operates, a presser foot to hold the Work during the punching operation, means for moving the punch alone and the anvil to feed the Work, and means for varying the amplitude of feed of each element between successive punching operations.

8. A perforating machine having mechanism for punching and feeding the work including separate devices movable successively between consecutive punching operations to advance the work, and a single controlling device whereby said devices may be rendered simultaneously ineffective for feeding the work.

9. A perforating machine having punching and feeding mechanism including a punch, an anvil and a presser foot cooperable with the anvil, said punch and said anvil and presser foot being movable successively to feed the work by consecutive steps, and means for simultaneously eliminating the feeding movements of the punch and of the anvil and presser foot without interrupting their other functions.

10. A perforating machine having a punch, an anvil, a presser foot cooperating with the anvil to hold the work, means for moving the punch transversely across the face of the anvil after the punching operation tofeed the work, and means for thereafter moving the anvil and presser foot together to feed the work further in t c same direction.

11. A perforating machine having a punch and an anvil, a presser foot cooperating with the anvil to engage the work therewith, means for moving the punch in one direction to feed the work while the anvil remains at rest, and means for moving the anvil and presser foot to feed the work further in the same direction while the punch is being moved in the opposite direction.

12. A perforating machine having an anvil, a punch member and a presser member movable each toward the work upon the anvil and then movable transversely, and means for moving the anvil transversely with the presser member to feed the work.

13. A perforating machine having an anvil, a punch and a presser member movable toward the work upon the anvil and also transversely to feed the work, a cam, two cam levers operatively connected to the cam at points in its periphery substantially 180 apart, and operating connections between the cam levers and the punch and presser member respectively.

14. A perforating machine having an anvil, a punch and a presser member relatively movable to engage the work, a cam, two cam levers operatively connected to the cam at points in its periphery 180 apart, and operating connections between one cam lever and the punch and between the other cam lever and the anvil for moving the two transversely and consecutively to feed the work.

15. A perforating machine having an anvil, a punch and a presser member, movable one after another to engage work upon the anvil, a cam, two cam levers operatively connected to the cam at separate points in its periphery, a link connection between one cam lever and the punch for effecting feed of the work by the punch, link connections between the other cam lever and the anvil and presser member for effecting feed of the work between the anvil and presser member independently of the feed of the punch, and means for simultaneously adjusting the link connections to vary the amplitude of feed.

16. A perforating machine having a frame, an anvil, a punch movably mounted in the frame, cam actuated mechanism for moving the punch toward the anvil and then transversely to feed actuated mechanism for moving the punch toward the anvil and then transversely to feed the work, and spring members for retracting the punch arranged to make rolling engagement with the frame during the feeding operation.

18. A perforating machine having a frame, an anvil, a punch movably mounted in the frame, cam actuated mechanism for moving the punch toward the anvil and then transversely to feed the work, a spring plunger arranged at each side of the axis of the punch for retracting the punch, and stationary ways in the frame carrying antifriction rolls for supporting said plungers.

19. A perforating machine having means for punching and feeding the work, a shaft angularly disposed to the direction of feed, a bracket slidably and rotatably mounted thereon for movement into and out of operative position relatively to the punching and feeding means, an edge guide carried by the bracket adapted to engage the work when the bracket is in operative position, and means for locating said bracket in predetermined operative position after a movement into inoperative position.

ZG. A perforating machine having means for punching and feeding the work, and an edge gage comprising an angularly adjustable bracket, an arm having an edge guiding surface mounted upon the bracket for adjustment in the direction of the work feeding movement, an overhanging foot adjustable heightwise of said arm and means holding the foot in fixed position relatively to the arm.

21. In a perforating machine having a cooperating punch and anvil in which the punch is moved toward and from the anvil to punch, then to release the anvil and then to release the work, means for independently adjusting the final punching position of the punch, its anvil-releasing position and its work-releasing position.

22. A perforating machine having an anvil, a punch movable to punch the work on the anvil and then to release the anvil for a work feeding step, separate cams for determining the punching strok and the releasing movement of the punch, and means for moving the punch transversely to feed the work.

23. A perforating machine having an anvil, a cooperating punch, a cam lever for moving the punch toward the anvil to punch the work, yielding means for retracting the punch, means for adjusting the cam lever to vary the point of nearest approach of the punch to the anvil, and an adjustable stop for positively limiting the retracting movement of the punch from the work.

24. A perforating machine having an anvil, a cooperating punch, a cam lever having two cam rolis mounted therein, a cam acting on one roll for moving the punch toward the anvil, means for adjusting the cam lever to vary the point of nearest approach of the punch and anvil, a second cam acting on the other cam roll for controlling the releasing movement of the punch from the anvil, and means for adjusting said roll in said cam lever.

25. A perforating machine having an anvil, a cooperating punch, a cam lever having two cam rolls mounted therein, a cam acting on one roll for moving the punch toward the anvil, means for adjusting the cam lever to vary the point of nearest approach of the punch and anvil, a sec- 0nd cam adjustably related through said second cam roll to the cam lever for controlling the releasing movement of the punch from the anvil, and adjustable means for controlling the disengaging movement of the punch from the work.

26. A perforating machine having cooperating punch and anvil, a carrier, a punch spindle rotatably mounted in the carrier and having a fiat surface thereon, means for transversely moving the carrier to feed the work, a rocker member arranged to engage the fiat surface of the spindle in one position of the carrier, an adjustable stop for determining the position of the rocker memher, and yielding means for holding said member against the stop.

27. A perforating machine having cooperating punch and anvil, a carrier, a punch spindle rotatably mounted in the carrier and having a flat surface thereon, and means for imparting a transverse work feeding movement to the carrier, a rocker member arranged to swing in the path of movement of the spindle and having a spindlepositioning face for cooperating with the fiat surface of the spindle, and separate adjusting and actuating means for the rocker member.

28. A perforating machine having an anvil, a punch, means for causing the punch to engage the work upon the anvil and to feed it transversely thereon, means for feeding a. backing strip across the anvil, and a single controlling device for regulating the rates of he work feed and the strip feed.

'29. A perforating machine having an anvil, a punch, means for moving the punch transversely to feed the work upon the anvil, means for imparting to the work a further feeding movement independently of the punch, and means for feeding a backing strip across the anvil during substantially the entire feeding movement of the work.

30. A perforating machine having a punch and clamping means including an anvil each movable to engage the work and then movable transversely of the Work, strip feeding means for advancing a backing strip across the anvil, an actuating cam and two trains of mechanism operated thereby, one for the punch and one for the anvil and both being arranged to operate the strip feeding means.

31. A perforating machine having a punch and a Work-engaging device comprising an anvil movable one after the other successively to feed the work, strip feeding means including a one-Way clutch, and means for advancing the clutch simultaneously with the movement of the punch and then with the movement of the work-engaging device.

32. A perforating machine having a punch and a work-engaging device comprising an anvil movable one after the other successively to feed the work, strip feeding means including a one-way clutch, means for advancing the clutch when the punch is moved and also when the anvil is moved in the feeding operation, and a controlling device for simultaneously regulating all of said movements.

33. A perforating machine having a fiat anvil, a punch arranged to reciprocate above the anvil, and mechanism for conducting a backing strip across the anvil including a supply reel arranged to rotate about a vertical axis, means for guiding the backing strip with a quarter turn to the anvil, a rewinding reel for receiving the used strip, and a feed roll driven in synchronism with punch movements.

FRANK BYCROFT KEALL.

CERTIFICATE OF CORRECTION.

Patent No. 1,943,441. January 16, 1934.

FRANK BYCROFT KEALL.

It is hereby certified that error appears in the printed specification of the above numbered patent requiring correction as follows: Page 3, line 36, after "of" second occurrence insert the word downward; page 7, line 37, claim 12, strike out the word "each" and insert the same before "movable" in line 36; and that the said Letters Patent should be read with these corrections therein that the same may conform to the record of the case in the Patent Office.

Signed and sealed this 20th day of March, A. D. 1934,

F. M. Hopkins (Seal) Acting Commissioner of Patents. 

